KR20000008676A - Resonator of rotary compressor - Google Patents
Resonator of rotary compressor Download PDFInfo
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- KR20000008676A KR20000008676A KR1019980028598A KR19980028598A KR20000008676A KR 20000008676 A KR20000008676 A KR 20000008676A KR 1019980028598 A KR1019980028598 A KR 1019980028598A KR 19980028598 A KR19980028598 A KR 19980028598A KR 20000008676 A KR20000008676 A KR 20000008676A
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2/00—Rotary-piston machines or pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/06—Silencing
- F04C29/061—Silencers using overlapping frequencies, e.g. Helmholtz resonators
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/0027—Pulsation and noise damping means
- F04B39/0055—Pulsation and noise damping means with a special shape of fluid passage, e.g. bends, throttles, diameter changes, pipes
- F04B39/0066—Pulsation and noise damping means with a special shape of fluid passage, e.g. bends, throttles, diameter changes, pipes using sidebranch resonators, e.g. Helmholtz resonators
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
- F04C23/008—Hermetic pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/06—Silencing
- F04C29/068—Silencing the silencing means being arranged inside the pump housing
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
- F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
- F04C18/3562—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation
- F04C18/3564—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation the surfaces of the inner and outer member, forming the working space, being surfaces of revolution
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10S181/00—Acoustics
- Y10S181/403—Refrigerator compresssor muffler
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T137/00—Fluid handling
- Y10T137/7722—Line condition change responsive valves
- Y10T137/7837—Direct response valves [i.e., check valve type]
- Y10T137/7879—Resilient material valve
- Y10T137/7888—With valve member flexing about securement
- Y10T137/7891—Flap or reed
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
Description
본 발명은 로터리 압축기에 관한 것으로서, 특히 저주파수 대역의 소음을 저감함과 동시에 압력맥동의 원활한 유입을 도모하여 실린더 내부의 압축실에서 발생하는 압력맥동에 기인하는 충격 가진력 및 맥동소음의 발생문제를 해결하기 위한 공명기의 구조에 관한 것이다.The present invention relates to a rotary compressor, in particular, to reduce the noise in the low frequency band and at the same time to facilitate the smooth inflow of pressure pulsation solves the problem of the generation of shock excitation force and pulsation noise caused by the pressure pulsation generated in the compression chamber inside the cylinder It relates to the structure of a resonator for.
일반적인 로터리 압축기는 도 1 에 도시된 바와 같이, 밀폐용기(1) 내에 압축기구부와 이를 구동하는 전동기구부로 구성된다.As shown in FIG. 1, a general rotary compressor includes a compression mechanism unit and an electric drive unit for driving the same in the sealed container 1.
상기 전동기구부는 전원이 인가되면 자력을 발생시키는 고정자(2)와, 상기 고정자(2)와의 상호 작용을 통해 발생되는 유도기전력에 의해 회전하는 회전자(3)와, 상기 회전자(3)에 압입되어 회전자(3)의 회전에 따라 회전하는 크랭크축(4)으로 구성된다.The electric machine part is a stator (2) for generating a magnetic force when the power is applied, the rotor (3) rotated by the induced electromotive force generated through the interaction with the stator (2), and the rotor (3) It consists of a crankshaft 4 which is press-fitted and rotates according to the rotation of the rotor 3.
상기 압축기구부는 도 2 와 같이, 상기 크랭크축(4)의 하부에 편심 축설되어 크랭크축(4)의 회전에 따라 일정한 편심궤적을 갖고 회전하면서 냉매를 흡입, 압축, 토출하는 롤러(5)와, 상기 롤러(5)의 작용공간이 되는 실린더(6)와, 상기 실린더(6)의 상, 하부에서 압축기구부를 지지하는 메인 베어링(7) 및 서브 베어링(8)과, 상기 롤러(5)의 회전에 따라 실린더(6)에 형성되어 있는 슬롯(9) 내를 왕복운동하면서 흡입실(10)과 압축실(11)을 분리하는 베인(12)과, 상기 실린더(6)로 흡입 및 토출되는 냉매의 유동 통로를 이루는 흡입구(13) 및 토출구(14)와, 상기 토출구(14)의 상부에 형성되어 토출 소음을 저감하는 머플러(15)로 구성된다.As shown in FIG. 2, the compressor mechanism is eccentrically arranged in the lower portion of the crankshaft 4, and has a constant eccentric trajectory in accordance with the rotation of the crankshaft 4, while the roller 5 sucks, compresses, and discharges the refrigerant. And a cylinder (6) serving as a working space of the roller (5), a main bearing (7) and a sub bearing (8) for supporting the compression mechanism on the upper and lower portions of the cylinder (6), and the roller (5). The vane 12 separating the suction chamber 10 and the compression chamber 11 while reciprocating in the slot 9 formed in the cylinder 6 in accordance with the rotation of the cylinder 6, suction and discharge to the cylinder (6) It consists of a suction port 13 and a discharge port 14 forming a flow passage of the refrigerant to be formed, and a muffler 15 formed on the discharge port 14 to reduce the discharge noise.
그리고, 도 3 과 같이 토출유체의 도입부에는 상기 토출구(14)와 연통되어 공명기(16)가 설치되는데, 상기 공명기(16)는 실린더(6)내에서 발생되는 압력맥동의 유입통로 역할을 하는 목부(16a)와, 상기 목부(16a)를 통해 유입된 압력맥동을 완화시키는 공명부(16b)로 구성된다.In addition, as shown in FIG. 3, a resonator 16 is installed at the introduction portion of the discharge fluid in communication with the discharge port 14, and the resonator 16 serves as an inflow passage for the pressure pulsation generated in the cylinder 6. And a resonance portion 16b for alleviating the pressure pulsations introduced through the neck portion 16a.
이와 같이 구성된 상태에서 축(4)의 회전에 따라 롤러(5)가 일정한 편심괘적을 그리면서 실린더(6) 내주면을 따라 자전 및 공전하기 시작하면 흡입력이 발생하여 냉매가 흡입구(13)를 통해 실린더(6)의 흡입실(10) 내로 유입되고, 상기 롤러(5)가 일정각 이상으로 회전하게 되면 냉매의 압축이 시작되며, 상기 롤러(5)의 회전각이 200°근방에 왔을 때 압축실(11) 내의 압력이 토출압과 같거나 커지게 되어 토출구(14)의 토출밸브(도면상에 미도시)가 열리고, 압축 냉매의 토출이 이루어지게 된다.In this configuration, when the roller 5 starts to rotate and revolve along the inner circumferential surface of the cylinder 6 while the roller 5 draws a certain eccentricity as the shaft 4 rotates, a suction force is generated, and the refrigerant flows through the inlet 13. When the roller 5 is rotated by a predetermined angle or more, the refrigerant begins to be compressed, and when the rotation angle of the roller 5 is about 200 °, the compression chamber is introduced into the suction chamber 10 of (6). The pressure in 11 is equal to or larger than the discharge pressure, so that a discharge valve (not shown in the figure) of the discharge port 14 is opened, and discharge of the compressed refrigerant is performed.
상기 토출구(14)를 통해 토출된 냉매는 메인 베어링(7) 상부의 머플러(15)로 유입되고, 이 머플러(15)는 토출 냉매의 소음을 저감하는 역할을 수행하게 된다.The refrigerant discharged through the discharge port 14 is introduced into the muffler 15 on the main bearing 7, and the muffler 15 serves to reduce noise of the discharge refrigerant.
이때, 상기 실린더(6)의 내부에서 이루어지는 냉매의 압축 및 토출과정에서 발생하는 압력 맥동에 의하여 충격 진동이 발생하고, 이러한 가진력이 압축부 구성 요소 부품들의 요동에 의한 진동을 발생시키게 되며, 실린더(6)의 외부로 전파되어 상기 실린더(6)와 용접되어 있는 밀폐용기(1)를 진동시킴으로써 압축기 외부로 소음이 누설된다.At this time, the impact vibration is generated by the pressure pulsation generated during the compression and discharge of the refrigerant inside the cylinder (6), the excitation force is generated by the vibration of the components of the compression unit, the cylinder ( Noise is leaked to the outside of the compressor by vibrating the sealed container 1 which is propagated outside of 6) and welded to the cylinder 6.
또한, 상기 실린더(6) 내부에서 발생한 냉매의 고주파 압력맥동 성분들이 토출시 압축기 내부 공간으로 급격히 팽창되면서 내부공간의 음향모드를 가진함으로써 압축기 외부로 강한 지향성을 갖는 공명음을 방사하는 소음원으로 작용하게 된다.In addition, the high frequency pressure pulsation components of the refrigerant generated inside the cylinder 6 expand rapidly into the compressor internal space during discharge, and thus have an acoustic mode of the internal space to act as a noise source that emits resonance sound having a strong directivity outside the compressor. do.
도 3 은 이를 해결하기 위해 토출유체의 도입부에 토출구(14)와 연통되어 있는 공명기(16)를 나타낸 것으로서, 상기 공명기(16)는 압축과정에서 발생하는 냉매의 압력맥동을 완화시키고, 토출시 압력맥동이 급격하게 유출되는 것을 방지하여 토출관련 소음 및 진동을 저감시키는 역할을 수행하게 된다.3 shows a resonator 16 in communication with the discharge port 14 at the inlet of the discharge fluid to solve this problem, the resonator 16 relieves the pressure pulsation of the refrigerant generated during the compression process, the pressure during discharge The pulsation is prevented from rapidly flowing out and serves to reduce the discharge-related noise and vibration.
이때, 상기 공명기의 목부(16a)와 공명부(16b)의 형상에 따라 공명기(16)로서의 소음 저감 작용이 발생하는 주파수 영역이 결정된다.At this time, the frequency range in which the noise reduction action as the resonator 16 occurs is determined according to the shapes of the necks 16a and 16b of the resonator.
일반적으로 인간의 청각이 가장 민감하게 반응하는 주파수는 4㎑로 알려져 있으며, 압축실(11) 내부의 고압 냉매가 그 소음원으로 작용하는 것으로 추정된다.In general, the frequency at which human hearing responds most sensitively is known to be 4 kHz, and the high-pressure refrigerant inside the compression chamber 11 is assumed to act as the noise source.
따라서 종래의 공명기(16)에 있어서 주로 고려되는 소음 주파수는 4㎑ 부근의 주파수 대역이며, 효율의 저하를 수반하지 않는 범위에서 목표 주파수에 대응하도록 목부(16a)와 공명부(16b)의 사양을 결정하게 된다.Therefore, the noise frequency mainly considered in the conventional resonator 16 is a frequency band around 4 kHz, and the specifications of the neck 16a and the resonator 16b are adapted so as to correspond to the target frequency within a range not accompanied by a decrease in efficiency. Will be decided.
그러나, 이러한 종래의 공명기는 토출구와 통해있는 목부의 압력맥동 도입부가 각진 형상을 이루므로 공명부측으로 유입되는 압력맥동 성분이 이 부위에 충돌하여 와류가 발생되며, 이로 인해 압축냉매의 토출이 원활하지 못하게 될 뿐만 아니라 유동소음이 증가되는 문제점이 있었다.However, such a conventional resonator has an angular shape of the pressure pulsation introduction portion of the neck through the discharge port, so that the pressure pulsation component flowing into the resonator part collides with this region, and vortex is generated. Not only was there a problem that the flow noise was increased.
또한, 최근 압축기의 대형화 추세에 따라 실린더의 압축공간이 증가하고 압축부를 구성하는 부품 및 최종적으로 소음을 방사하는 밀폐용기의 크기가 커지면서 압축기로부터 방사되는 소음의 주요 주파수 성분이 저주파대역으로 이동하는 현상이 나타나게 된다.In addition, as the size of the compressor increases in recent years, the compression space of the cylinder increases, the size of the components constituting the compression unit and the size of the sealed container that finally emits noise increases, and the main frequency components of the noise radiated from the compressor move to the low frequency band. Will appear.
이러한 경향에 따라 종래 4㎑ 주파수 대역에 주목하여 설계된 공명기를 대형 모델에 적용하는 데에 한계가 발생되며, 압축실의 용적에 따라 적절한 사양의 공명기를 적용하는 것이 요구되었다.According to this tendency, there is a limit in applying a resonator designed to the conventional 4 kHz frequency band to a large model, and it is required to apply a resonator having an appropriate specification according to the volume of the compression chamber.
특히, 압축기가 에어컨 세트에 장착되는 경우 4㎑ 부근의 고주파 소음 성분에 대해서는 흡차음재 등을 적절히 사용하여 효과를 나타내는 반면 비교적 주파수대가 낮은 소음 성분에 대해서는 차음효과가 저하되기 때문에 오히려 사용자에게 거슬리는 소음을 유발하는 문제가 발생되었다.In particular, when the compressor is installed in the air conditioner set, the sound absorbing and insulating material is used for the high frequency noise component near 4 kHz, and the sound insulation effect is lowered for the noise component having a relatively low frequency band. A provoking problem has occurred.
본 발명은 이러한 점을 감안하여 제안된 것으로, 실제 사람의 귀에 거슬리는 주요 소음원인 저주파수 대역의 소음성분에 대응할 수 있는 구조의 공명기를 제공함과 동시에 압축실에서 발생된 압력맥동 성분의 공명기측 유입을 원활히 함으로써 압력맥동에 기인하는 충격 가진력 및 맥동소음의 발생문제를 해결하는 데 그 목적이 있다.The present invention has been proposed in view of this point, and provides a resonator of a structure capable of responding to low frequency band noise components, which are annoying to the real human ear, and at the same time smoothly introduces the resonator side inflow of pressure pulsating components generated in the compression chamber. Therefore, the purpose is to solve the problem of the impact vibration and pulsation noise caused by the pressure pulsation.
이러한 목적을 달성하기 위해 본 발명은 축의 회전에 따라 일정한 편심 궤적을 갖고 회전하면서 냉매를 흡입, 압축, 토출하는 롤러와, 상기 롤러의 작용공간을 이루는 실린더와, 상기 실린더의 상, 하부에서 이를 지지하는 메인 베어링 및 서브 베어링과, 압축 냉매의 토출 통로인 토출구와, 상기 토출구를 개폐하는 토출밸브와, 상기 토출밸브의 상부에 형성되어 냉매의 토출 소음을 줄여주는 머플러와, 냉매의 압축과정에서 발생되는 압력맥동을 완화시키기 위한 공명기로 구성되며, 상기 공명기는 토출구와 연통되어 압력맥동 성분의 유입 통로를 이루는 목부와, 상기 목부를 통해 유입된 압력맥동 성분을 완화시키는 공명부로 구성된 로터리 압축기의 압축기구부에 있어서, 상기 공명기가 저주파수 대역의 소음에 대응할 수 있도록 토출구 직경과 공명부 직경의 비는 1.2∼1.8 : 1로 구성되고, 상기 공명부의 직경과 높이의 비는 1.0∼2.5 : 1로 구성되며, 상기 목부 길이와 상기 공명부 높이의 비는 0.6∼1.2 : 1로 구성되고, 상기 목부의 길이와 직경의 비는 1.5∼2.8 : 1로 구성된 것을 특징으로 한다.In order to achieve the above object, the present invention supports a roller which sucks, compresses, and discharges a refrigerant while rotating with a certain eccentric trajectory according to the rotation of the shaft, a cylinder constituting the working space of the roller, and upper and lower portions of the cylinder. A main bearing and a sub bearing, a discharge port serving as a discharge passage of the compressed refrigerant, a discharge valve for opening and closing the discharge port, a muffler formed at an upper portion of the discharge valve to reduce discharge noise of the refrigerant, and a process of compressing the refrigerant. Compressor section of the rotary compressor consisting of a resonator for relieving the pressure pulsation component, the resonator is in communication with the discharge port to form an inlet passage of the pressure pulsating component, and a resonator for relieving the pressure pulsating component introduced through the neck The discharge diameter and the resonance of the resonator so that the resonator can respond to the noise of the low frequency band The ratio of the minor diameter is 1.2 to 1.8: 1, the ratio of the diameter and the height of the resonator is 1.0 to 2.5: 1, and the ratio of the length of the neck and the height of the resonator is 0.6 to 1.2: 1. The ratio of the length and the diameter of the neck portion is characterized by consisting of 1.5 to 2.8: 1.
도 1 은 일반적인 로터리 압축기의 구성도.1 is a block diagram of a typical rotary compressor.
도 2 는 종래 로터리 압축기의 압축기구부 구성도.Figure 2 is a configuration diagram of the compression mechanism of the conventional rotary compressor.
도 3 은 종래 로터리 압축기의 토출계 구성도.3 is a configuration diagram of a discharge system of a conventional rotary compressor.
도 4 는 본 발명에 의한 로터리 압축기의 토출계 구성도.4 is a configuration diagram of a discharge system of a rotary compressor according to the present invention.
도 5 는 본 발명에 의한 로터리 압축기의 공명기 상세도.5 is a detailed view of a resonator of a rotary compressor according to the present invention.
도 6 은 본 발명에 의한 공명기의 소음 저감 특성을 나타낸 그래프.6 is a graph showing the noise reduction characteristics of the resonator according to the present invention.
*** 도면의 주요 부분에 대한 부호의 설명 ****** Explanation of symbols for the main parts of the drawing ***
101 : 실린더 102 : 토출구101: cylinder 102: discharge port
103 : 공명기 103a : 목부103: resonator 103a: neck
103b : 공명부 103c : 곡면부103b: resonance portion 103c: curved portion
이하, 본 발명을 첨부한 도면에 의거하여 상세히 설명하면 다음과 같다.Hereinafter, the present invention will be described in detail with reference to the accompanying drawings.
도 4 는 본 발명에 의한 로터리 압축기의 압축기구부 구성도로서, 롤러(도면상에는 도시되지 않음)에 의해 냉매를 흡입, 압축, 토출하는 공간을 이루는 원통형의 실린더(101)와, 상기 실린더(101)에서 압축된 냉매를 토출하기 위한 토출구(102)가 구비되며, 상기 토출구(102)와 연통되어 공명기(103)가 실린더(101) 또는 베어링부(도면상에는 도시되지 않음)에 형성된다.4 is a configuration diagram of a compression mechanism of a rotary compressor according to the present invention, wherein a cylindrical cylinder 101 forming a space for sucking, compressing, and discharging a refrigerant by a roller (not shown in the drawing) and the cylinder 101 are shown. The discharge port 102 for discharging the compressed refrigerant in the air is provided, the resonator 103 is formed in the cylinder 101 or the bearing portion (not shown) in communication with the discharge port (102).
또한, 도 5 와 같이 상기 공명기(103)는 목부(103a)와 공명부(103b)로 나누어지는데, 상기 목부(103a)는 압력맥동 성분의 유입 통로를 이루며, 상기 공명부(103b)는 목부(102a)를 통해 유입된 압력맥동 성분을 완화시켜 소음을 저감하는 역할을 수행하게 된다.In addition, the resonator 103 is divided into a neck (103a) and a resonator (103b), as shown in Figure 5, the neck (103a) forms an inflow passage of the pressure pulsating component, the resonator (103b) is a neck ( The pressure pulsation component introduced through 102a) serves to reduce noise.
이때, 상기 공명기(103)는 저주파수 대역(0.5∼2.0㎑ 대역)의 소음 성분 저감에 주목하여 설계한 것으로, 토출구(102) 직경과 공명부(103b) 직경의 비는 1.2∼1.8 : 1로, 상기 공명부(103b)의 직경과 높이의 비는 1.0∼2.5 : 1로, 목부(103a) 길이와 상기 공명부(103b) 높이의 비는 0.6∼1.2 : 1로, 상기 목부(103a)의 길이와 직경의 비는 1.5∼2.8 : 1로 구성하게 된다.At this time, the resonator 103 is designed to pay attention to the noise component reduction of the low frequency band (0.5 ~ 2.0 kHz band), the ratio of the diameter of the discharge port 102 and the diameter of the resonator 103b is 1.2 to 1.8: 1, The ratio of the diameter and height of the resonance portion 103b is 1.0 to 2.5: 1, and the ratio of the length of the neck portion 103a and the height of the resonance portion 103b is 0.6 to 1.2: 1, the length of the neck portion 103a. The ratio of and diameter is 1.5 to 2.8: 1.
또한, 상기 공명기 목부(103a)의 압력맥동 도입부에는 압력맥동 성분이 그 끝단에 부딪혀 발생되는 와류 현상을 억제하여 압력맥동 성분이 공명부(103b)측으로 원활하게 유입될 수 있도록 곡면부(103c)가 형성되며, 이에 따른 소음저감 효과를 최대한 얻기 위해 구체적으로는 곡면부(103c)의 반경과 목부(103a)의 직경의 비가 2.5∼3.5 : 1이 되도록 구성한다.In addition, in the pressure pulsation introduction portion of the resonator neck 103a, a curved portion 103c is provided so that the pressure pulsation component can be smoothly introduced into the resonance portion 103b side by suppressing the vortex phenomenon caused by the pressure pulsation component hitting the end thereof. In order to obtain the maximum noise reduction effect, the ratio of the radius of the curved surface portion 103c and the diameter of the neck portion 103a is 2.5 to 3.5: 1.
이와 같이 구성된 본 발명의 작용을 설명하면 다음과 같다.Referring to the operation of the present invention configured as described above is as follows.
먼저, 본 발명에 의한 공명기는 종래 공명기 설계에 있어서 소음저감 목표 주파수 설정에 따른 문제를 해결하기 위한 것으로, 압축기의 소음 특성에 따른 최대의 소음 저감 효과를 도모하고자 압축실 내부에서 발생하는 저주파 압력맥동 성분에 주목하여 설계한 것이다.First, the resonator according to the present invention is to solve the problem according to the noise reduction target frequency setting in the conventional resonator design, low frequency pressure pulsation generated in the compression chamber to achieve the maximum noise reduction effect according to the noise characteristics of the compressor It is designed with attention to the components.
즉, 로터리 압축기의 실린더(101) 내에서 롤러가 실린더(101) 내주면을 편심회전함에 따라 냉매의 압축 및 토출을 반복하는 과정에서 주기적으로 발생하는 저주파수 대역(0.5∼2.0㎑)의 소음 성분을 저감하기 위하여 토출구(102) 부근의 베어링면 또는 실린더(101)면에 공명공간을 형성함에 있어, 토출구(102) 직경과 공명부(103b) 직경의 비는 1.2∼1.8 : 1로, 상기 공명부(103b)의 직경과 높이의 비는 1.0∼2.5 : 1로, 목부(103a) 길이와 상기 공명부(103b) 높이의 비는 0.6∼1.2 : 1로, 상기 목부(103a)의 길이와 직경의 비는 1.5∼2.8 : 1로 구성함으로써 종래 고주파수 대역(주로 4㎑ 대역)의 소음 저감에만 주력하였던 것과 비교하여 실제 사람의 귀에 거슬리는 주요 소음원인 저주파수 대역(0.5∼2.0㎑ 대역)의 소음을 용이하게 저감할 수 있어 종래의 소형 로터리 압축기에 적용할 경우에도 최대의 소음 저감능력을 발휘할 수 있으며, 특히 저주파수 대역의 소음이 많이 발생되는 대형 로터리 압축기에 적용이 가능해지게 된다.In other words, as the roller eccentrically rotates the inner circumferential surface of the cylinder 101 in the cylinder 101 of the rotary compressor, the noise component of the low frequency band (0.5 to 2.0 kHz) periodically generated during the process of repeatedly compressing and discharging the refrigerant is reduced. In order to form a resonance space on the bearing surface or cylinder 101 surface near the discharge port 102, the ratio of the diameter of the discharge hole 102 to the diameter of the resonance part 103b is 1.2 to 1.8: 1, and the resonance part ( The ratio of the diameter and height of 103b) is 1.0 to 2.5: 1, and the ratio of the length of the neck 103a and the height of the resonance portion 103b is 0.6 to 1.2: 1, and the ratio of the length and diameter of the neck 103a. By setting 1.5 to 2.8: 1, the noise in the low frequency band (0.5 to 2.0 kHz), which is a major noise source that is uncomfortable to the human being, is easily reduced, compared to the conventional high frequency band (mainly 4 kHz). Can be applied to conventional small rotary compressor Yiwu also may exhibit a maximum noise reduction capability of, becomes particularly possible to apply a larger rotary compressors that generate a lot of noise in the low frequency band.
또한, 본 발명에 의한 공명기(103)의 목부(103a)에 형성되어 있는 곡면부(103c)는 실린더(101)의 압축실에서 발생된 압력맥동의 와류발생을 억제하여 압력맥동 성분이 공명부(103b)측으로 원활하게 유입되도록 하기 위한 것으로서, 도 6 에 도시된 바와 같이 상기 곡면부(103c)의 반경과 목부(103a)의 직경 비에 따라 공명기의 소음 저감 특성이 변하게 되며, 가장 효과적인 소음 저감 특성을 발휘하기 위하여 곡면부의 반경과 목부 직경의 비를 2.5∼3.5 : 1로 구성하게 된 것이다.Further, the curved portion 103c formed in the neck portion 103a of the resonator 103 according to the present invention suppresses the vortex generation of the pressure pulsation generated in the compression chamber of the cylinder 101 so that the pressure pulsation component is resonated ( As to smoothly flow into the 103b) side, as shown in Figure 6, the noise reduction characteristics of the resonator is changed according to the radius ratio of the radius of the curved portion 103c and the diameter of the neck 103a, the most effective noise reduction characteristics In order to achieve the ratio of the radius of the curved portion and the diameter of the neck portion is to be composed of 2.5 to 3.5: 1.
이상에서 설명한 바와 같이 본 발명은 실제 사람의 귀에 거슬리는 주요 소음원인 저주파수 대역(0.5∼2.0㎑ 대역)의 소음에 주목하여 공명기를 설계함으로써 종래의 소형 로터리 압축기에 적용할 경우에도 최대의 소음 저감능력을 발휘할 수 있으며, 특히 저주파수 대역의 소음이 많이 발생되는 대형 로터리 압축기에 적용이 가능해지는 효과가 있다.As described above, the present invention designs a resonator by paying attention to the low frequency band (0.5 to 2.0 GHz band), which is a major noise source that is annoying to the actual human ear, so that even when applied to a conventional small rotary compressor, the maximum noise reduction ability is achieved. It can be exhibited, in particular, there is an effect that can be applied to a large rotary compressor that generates a lot of noise in the low frequency band.
또한, 압력맥동 성분의 유입통로를 이루는 공명기의 목부에 곡면부를 형성함으로써 압력맥동 성분의 와류를 억제하게 되어 압축냉매의 원활한 유입을 도모함과 동시에 소음 저감 특성을 최대한 발휘할 수 있는 효과가 있다.In addition, by forming a curved portion in the neck of the resonator constituting the inlet passage of the pressure pulsating component to suppress the vortex of the pressure pulsating component to facilitate the smooth inflow of the compressed refrigerant and at the same time have the effect to maximize the noise reduction characteristics.
Claims (3)
Priority Applications (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| KR1019980028598A KR100286837B1 (en) | 1998-07-15 | 1998-07-15 | Resonator of a rotary compressor |
| US09/333,958 US6176687B1 (en) | 1998-07-15 | 1999-06-16 | Resonator for rotary compressor |
| CNB991095979A CN1270104C (en) | 1998-07-15 | 1999-07-13 | Resonator for rotary compressor |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| KR1019980028598A KR100286837B1 (en) | 1998-07-15 | 1998-07-15 | Resonator of a rotary compressor |
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| KR20000008676A true KR20000008676A (en) | 2000-02-15 |
| KR100286837B1 KR100286837B1 (en) | 2001-05-02 |
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|---|---|
| US (1) | US6176687B1 (en) |
| KR (1) | KR100286837B1 (en) |
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| KR100688671B1 (en) * | 2005-11-30 | 2007-03-02 | 엘지전자 주식회사 | Noise reducing structure for scroll compressor |
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| JP6094236B2 (en) * | 2013-01-30 | 2017-03-15 | 株式会社デンソー | Compressor |
| EP3161295A4 (en) * | 2014-06-30 | 2018-03-21 | Cummins, Inc. | System and method for valve size ratio and igniter placement |
| CN104088794A (en) * | 2014-07-15 | 2014-10-08 | 珠海凌达压缩机有限公司 | Exhaust device, compressor and air conditioner |
| CN106401965B (en) * | 2016-06-24 | 2019-03-22 | 珠海格力电器股份有限公司 | Exhaust bearing seat and screw compressor |
| JP6635095B2 (en) * | 2017-07-19 | 2020-01-22 | ダイキン工業株式会社 | Rotary compressor |
| CN107620712B (en) * | 2017-09-04 | 2024-09-13 | 河南中烟工业有限责任公司 | Exhaust silencer for eliminating intermittent pulse airflow noise |
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| KR102507786B1 (en) | 2018-08-21 | 2023-03-09 | 삼성전자주식회사 | A compressor and electronic device using the same |
| KR102476697B1 (en) * | 2021-02-01 | 2022-12-12 | 엘지전자 주식회사 | Rotary compressor |
| CN113183750A (en) * | 2021-04-29 | 2021-07-30 | 东风汽车集团股份有限公司 | Structure for sounding by using automobile exhaust, control method thereof and exhaust system tail pipe |
| CN114087182A (en) * | 2021-12-08 | 2022-02-25 | 珠海凌达压缩机有限公司 | Pump body structure, compressor and air conditioner |
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| US2229119A (en) * | 1939-09-20 | 1941-01-21 | American Locomotive Co | Venturi silencer |
| US3193193A (en) * | 1958-03-13 | 1965-07-06 | Carrier Corp | Compressor muffler construction and method for muffling compressor discharge gases |
| EP0135254B1 (en) * | 1983-06-24 | 1988-01-07 | Matsushita Refrigeration Company | Rotary compressor |
| DE3332259A1 (en) * | 1983-09-07 | 1985-03-28 | Danfoss A/S, Nordborg | REFRIGERATOR COMPRESSORS |
| JPH0768951B2 (en) * | 1987-01-20 | 1995-07-26 | 三菱重工業株式会社 | Rotary compressor |
| BR8901185A (en) * | 1989-03-09 | 1990-10-16 | Brasil Compressores Sa | DISCHARGE SYSTEM FOR ROTARY PISTON ROTARY COMPRESSOR |
| KR920007624B1 (en) * | 1990-10-22 | 1992-09-09 | 대우캐리어 주식회사 | Muffler for hermetic rotary compressor |
-
1998
- 1998-07-15 KR KR1019980028598A patent/KR100286837B1/en not_active IP Right Cessation
-
1999
- 1999-06-16 US US09/333,958 patent/US6176687B1/en not_active Expired - Lifetime
- 1999-07-13 CN CNB991095979A patent/CN1270104C/en not_active Expired - Fee Related
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR100688671B1 (en) * | 2005-11-30 | 2007-03-02 | 엘지전자 주식회사 | Noise reducing structure for scroll compressor |
Also Published As
| Publication number | Publication date |
|---|---|
| CN1270104C (en) | 2006-08-16 |
| US6176687B1 (en) | 2001-01-23 |
| CN1243204A (en) | 2000-02-02 |
| KR100286837B1 (en) | 2001-05-02 |
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